Vibrating apparatus



SRv afarsnse i n 0S@ March 30, 1948.

E. W.| ARS;I-:N

VIBRATING APPARATUS v1946 7 Sheets-Sheet l Filed March 27 ATTO/WYE? March 30, 1948.

E. W. LA RSEN VLBRATlNG APPARATUS 7 sheets-Sheet 3 Filed karen 27, 194e 4 TTORA/EY March 30,l 1948. E. w. LARSEN VIBHATING APPARATUS Filed`March 27, 1946 7 Sheets-Sheet 4 E. W. LARSEN vxnmvrma Ananus Filed March 27.

March 1946 7 Sheets-Sheet 6 CROSS REQRENCE E. W. LARSEN ViBRATING APPARATUS March 3o, 1948.

7 Sheets-Sheet 7 Filed March 27, 1946 A rramyfy Patented Mar. 30, 1948 UNITED STATES PATENT OFFICE- VIBRATING APPARATUS Einer W. Larsen, Elmhurst, Ill., assigner to Western Electric Company, Incorporated, New York, N. Y., a corporation of New York Application March 27, 1946, Serial No. 657,355

15 Claims. (C1. 74-26) 1 2 This invention relates to vibrating apparatus Mechanism is also provided for compensating for and more particularly to a vibrating machine for the elasticity of the various members connecting simulating the vibrations to which apparatus the eccentric bushings to the table whereby the In the manufacture of electrical apparatus for 5 Amentioned set-up may be controlled with a high use in airplanes, ships, et cetera, the apparatus degree of accuracy While varying the speed of the must be constructed to operate under all condidrive motor of the apparatus. Means is also tions to which it may be subjected in service provided for controlling the control motors time and, accordingly, it is necessary to test the apcycle, thereby to adjust the range of speed.

paratus while subjecting it to such vibrations A complete understanding of the invention and shocks as it may receive in use. There have may be had by reference to the following debeen various mechanisms built which attempted tailed description thereof when considered in to simulate the operating conditions to which connection with the accompanying drawings, in such electrical apparatus would be subjected, but which as far as is known, none of these mechanisms Fig. l is a fragmentary plan View of an apincludes means for compensating for the elasparatus embodying the features of the invention, ticity of various operating members of the mechthe apparatus being shown set up whereby the anism whereby the amplitude of vibrations of table may have imparted thereto either vertical the apparatus may be controlled with a high or horizontal or combined vertical and horizontal degree of accuracy While varying the rate of vibrations of Varying frequencies and eiiective to vibration over selected ranges. compensate for the inherent elasticityk of the An object of the present invention is to proconnections between the drive and the table in Vide a Simple and practicable apparatus for viorder to maintain constant the amplitude of bretlg alleles at predetermined amplitudes vibrations of the table at varying frequencies; and rates in simulation of various conditions to Fig. 2 is a side elevational View of the apwhich the articles may be subjected in service. paratus shown in Fig. 1, looking at the side In accordance with one embodiment of the of the apparatus as indicated by the line 2-2 invention, a reversible constant speed electric of Fig 1ln the direction of the arrows; control motor drives a pair of cams alternately Fig. 3 is a fragmentary plan sectional view in opposite directions to shift a main control taken either Substantially along the une 3 3 of lever for Controlling the amplitude of vigrgtions-. Fig. 2 or along the line 3-3 of Fig. 4, 1ooking Q La table Supporting articles being vibrated and .l in the direction of the arrows;

also drives a potentiometer brush back and forth Fig. 4 is an enlarged longitudinal Vertical Sec.. 1n a fixed path and'through a predetermlned tional view taken either substantially along the dlstance for controlling the frequency of the une 4 4 of Fig 3 or along the une 4 4 of Fig vibrations. The movement of the potentiometer 1 looking in the direction of the arrows. brush controls the speed of a main drive motor Fig. 5 1s a fragmentary 1ong1tud1nal vertical which determines the frequency of the vlbrations, whereas the main control lever selectively Sstsmnllyilewzataeisbra'n. alolg the; lge controls the degree of effective eccentricity vof 40 arrow? g o n 1 e rec lon o e either or Iboth of a pair of eccentric assemblies to cause horizontal or verticalv or, rotary move- Flg' 6 is a fragmentary Vertlcal Sectional View ment to bemparted wthe table. taken substantially along the line 6 6 of Fig. 3,

The apparatus may be Set up and operated to looking in the direction of the arrows; n Cause the table to vibrate either horizontally,- Figs. 'i end 8 are fragmentary vertical secvertically or through a circular path over a con.. tional views on reduced scales, taken substanstant amplitude and a selected range of fretially along the lines 1-1 and 8-8 of Fig. 4, quency, or at a constant rate of acceleration over looking in the direction of the arrows;

a selected range of frequency and to maintain Fig. 9 is a plan sectional view on a. reduced the selected rate of acceleration constant. 59 scale, partly broken away, taken substantially Iwill be subjected when in service. amplitude of vibrations of the table in the iirst- CiOSS 'REFERENCE along the line 9 9 of Fig. 4, looking in the direction of the arrows;

Fig. 10 is a fragmentary plan view of Fig. 3, showing the apparatus set up whereby the table may be vibrated at a constant rate of acceleration over a selected range of speed;

Fig. 1l is a fragmentary vertical sectional view taken along the line H-H of Fig. 10, looking in the direction of the arrows;

Fig. l2 is a fragmentary vertical sectional View taken substantially along the line I2-I2 of Fig. 3, or along the line lil-i2 of Fig. 4, looking in the direction of the arrows; and

Figs. 13 and 14 are greatly enlarged fragmentary detail vertical sectional views similar to Fig. 4, Fig. 13 showing the left-hand eccentric portion of the shaft unclutched from its associated bushing, which imparts horizontal vibrations to the table and thus no horizontal vibrations of the table will occur, the right-hand eccentric portion of the shaft being shown clutched to its associated bushing, whereby vertical vibrations of the table will occur; and Fig. 14 showing the left and right-hand eccentric portions of the shaft clutched and unclutched, respectively, to

and from their associated bushings whereby horizontal vibrations of the table alone will occur,

Before entering into the detailed description of all of the details of the preferred form of the apparatus, it may be noted that the main control lever, which controls the amplitude of vibrations of the table, is connected to a yokek member spanning a longitudinally xed shaft driven by the main drive motor and shiftable longitudinally of the shaft. A threaded or helically splined portion on the shaft has a nut thereon which is rotatable relative to the shaft, when moved axially thereon by the yoke member, the nut being splined to a sleeve surrounding and rotatable relative to the shaft and movable axially thereof. Surrounding eccentric portions formed on the shaft adjacent opposite ends of the sleeve are adjustableeccentric bushings, which are operatively connected to the support table, the bushings being so connected with the table that when riven by their associated eccentric shaft portions and dependent upon their eccentricity relative to the axis of the shaft, one Will cause a horizontal movement of the table and the other a vertical movement thereof or they may be so coupled together, if desired, to cause the table to move in circular paths of different diameters. Means including Oldham type couplings are provided for optionally clutching the sleeve at its opposite ends to either of the bushings or to both of the bushings at the same time to cause the abovementioned horizontal, vertical and circular movements of the table. The sleeve is shiftable axially of the shaft as desired by means of a hand operable rod movable along the axis of the shaft and connected to the sleeve. The arrangement of coupling the sleeve to only one of the bushings is such that when one bushing is in use to drive the table, the other bushing is set for Zero eccentricity with respect to the axis of the shaft and is locked against rotation with respect thereto by the interengagement of ar-key member keyed to the shaft and carrying teeth in the path of teeth on one of the members of the associated Oldham coupling, thus causing the bushing to rotate with the shaft without causing any motion to be transmitted thereby to the table. V

Means is provided for automatically shifting the yoke member whereby the nut carried on the shaft will be rotated and shifted axially relative to the shaft and thus the bushing surrounding the eccentric portion of the shaft and coupled to the nut through the sleeve and Oldham coupling will also be rotated to cause a variation in the eccentricity of the bushing relative to the axis of the shaft and thus a variation in the movement imparted thereby to the table as the shaft rotates.

In the specific embodiment of the invention chosen for illustration, apparatus is shown in Figs. 1 to 9, inclusive, and Figs. 12, 13 and 14 for vibrating a support table through a cycle of from, for example 60 to nearly 0 vibrations per second at a constant amplitude and including an elasticity compensating mechanism. In providing mechanism for accomplishing this effect, the mechanism includes a main base member t (Figs. 1 and 4) having an electric main drive motor 2| mounted upon it, a shaft 22 of the rnctor being in axial alignment with a main driving shaft 23 of the apparatus and directly connected thereto by a coupling 2d. The shaft 23 is jour nalled at opposite ends, each end having two reduced concentric portions, one end being journalled in ball and roller bearing assemblages 2? and 23, respectively, carried by a bearing block 29 and the other end being journalled in ball and roller bearing assemblages Sil and 3l, respectively, carried within a bearing block 33. The bearing blocks 29 and 33 are mounted in side frame members 34 and 35, respectively, suitably attached to the main base member i''the inner races of the roller bearing assemblages and Si being xed to bearing members 3S surrounding the inner reduced portions of the shaft. Adjoining the inner reduced concentric shaft portions are eccentric shaft portions dil and di surrounded by shouldered eccentric bushings 2 and Upon the outer peripheries of the bushings di and d3 are rotatably carried roller bearing assemblages 44 and 135, respectively, which are surrounded by bearing rings 43 and 439, respectively. The eccentric shaft portions t and di and the eccentric bushings fi?. and 63 are so proportioned that when the bushings are rotated to a predetermined lposition with respect to the shaft, the outer surfaces of the bushings will be concentric with the axis of the shaft and, when the bushings are in the predetermined position, rotation of the shaft will not result in movement being imparted to the bearing rings 3 and t9. The eccentric shaft portions dil and l are offset 9!) degrees from one another in order to obtain a circular motion of the table when such motion is desired and the eccentric bushings d2 and y be adjusted circularly upon their associated eccentric portions and di of the shaft '3 to adjust the effective eccentricity of the bushings with respect to the axis of the shaft or to provide zero eccentricity by means to be hereinafter described.

Extending from the lower side of the ring is an arm til and extending from the upper side of the ring 28 is an arm 5l (Figs. 4 and S). Since the bearing rings $8 and 43 surround the eccentric bushings d and '53, respectively, the eccentric motion of the bushings during the rotation of the shaft is transmitted to the rings and, consequently, to the arms 5i) 5|. The reciproca- OI'Y motions of the arm 59 are transmitted to an article support or table 52 to cause vertical reciprocations by the following interconnected leverage mechanism. Carried by the arm 5t is a pin 55 (Figs. 4 and 7) which extends at opposite ends therefrom and freely rotatably supports links 56-53 on its ends. The links '5S- 53, in turn, are connected to a pin 5l, which extends freely through an aperture 53 in the arm 5i). Journalled on the pin 55 are furcations Eil-59 of a bifurcated lever 82 and similarly associated with the pin 5l are furcations (i3-33 of a bifurcated lever 64. The two levers 62 and E4 extend horizontally in opposite directions and are integral with torque pivot tubes t5 and 36, respectively, pivoted at 69, to the side frame members 34 and 35 (Fig. 9). The tubes 85 and 66 are pivotally connected at 'lil to lower ends of rods 1|, which are pivotally connected at their upper ends at 'l2 to two corners of the table 52. The opposite ends of the tubes 65 and 5t are also connected at 13 (Fig. 8) to rods 'il pivotally connected at their upper ends at it to two opposite corners of the table.

In the operation of the apparatus, it will be apparent that the vertical reciprocations imparted to the arm 59 during the rotation of the eccentric portion 4| of the shaft 23 will be transmitted through the levers 52 and 54, the torque tubes 35 and EG, and the vertical rods simultaneously to the four corners of the table. apparent that the frequency of such vertical reciprocations of the table may be controlled by varying the revolutions per minute to the main driving shaft 23.

For imparting horizontal reciprocations to the table 52 from the vertical reciprocations imparted to the arm 5| during the rotation of the eccentric portion 40 of the shaft 23, the following interconnected leverage mechanism is provided. The arm 5|, which extends vertically from the upper side of the ring 43 (Figs. 4 and 8), is pivoted at 'i1 to a horizontally disposed lever 18 integral with a torque pivot tube 'i3 pivoted, directly above the tube 55 in a manner similar to that of the tubes 65 and 33, to the side frame members 34 and 35. Pivotally connected at 83 to opposite ends of the tube 'I9 are ends of horizontally extending rods 33, which are pivotally connected at their opposite ends at Sd to the table 52. It will be apparent, during the operation of the apparatus, that the vertical reciprocations imparted to the arm 5| during the rotation of the eccentric portion fill of the shaft 23 will be transmitted through the lever "i3, torque tube i3 and the horizontal rods 83 simultaneously to spaced points of the table 52, which points are arranged intermediate the vertical rods '1| and that the frequency of such horizontal reciprocations of the table may be controlled by varying the revolutions per minute of the main driving shaft 23,

It is to be noted that the table 52 never reciprocates in a truly horizontal or vertical plane due to the fact that it is always connected to both of the described leverage mechanisms; that is, when the table is being operated horizontally by the horizontal rods 83, it will be supported for horizontal movements by the vertical rods 1| and thus will move in a slightly arcuate path. Similarly, when the table is being operated vertically, the horizontal rods 83 will guide it in its vertical movements and it, therefore, will move in a slightly arcuate path. u

In order to impart'either horizontal or vertical movements to the table 52, the adjustable eccentric bushings 42 and 43 may be adjusted upon their corresponding eccentric shaft portions 40 and 4|, whereby, dependent upon their eccentricity relative to the axis of the shaft, either horizontal or vertical movements will be imparted to the table and the degree of eccentricity will con- It will also be.

trol the amplitude of movement of the table. The arrangement is such that when it is desired to impart either horizontal or vertical movements to.

the table 52, one bushing is set for zero eccentricity with respect to the axis of the shaft 23 and is locked against rotation with respect thereto.

To accomplish this optional adjustment of the eccentric bushings 42 and 43, the following mechanism is provided. Associated with each of the bushings 42 and 43 are Oldham type couplings 35 and 8S, respectively. The Oldham couplings are of exactly the same construction and, therefore, only one of them, coupling 85, associated with the eccentric bushing 42, will be described in detail herein. This coupling comprises an annular radially floating member 81 having a plurality of teeth or keys 9| and 92 (Figs. 4, 13 and 14) extending at right angles oneto another from opposite annular end faces thereof and projecting into radial keyways 93 and S4 formed in the opposed end faces of an Oldham clutch bushing 91 and the eccentric bushing 42, which also serves as a part of the Oldham coupling, whereby the coupling 85 will serve to interconnect the bushing 42 and the bushing 91 for rotation together, but will vpermit the bushing 42 to be moved eccentrically of the axis of the shaft 23 in a manner to be presently described. The annular toothed members 87 and the clutch bushings 91 of the couplings 35 and 85 surround concentric portions 93 of the shaft 23, the latter shaft portions being contiguous at opposite ends with the eccentric shaft portions 4| and 42 and a central concentric portion 99 of greatest diameter of the shaft,

Surrounding the central shaft portion 99 is a rotatable and longitudinally movable clutch sleeve |38, which is rotatably supported upon flanged sleeves IBI and |32, which are connected to the sleeve |03 for longitudinal movement therewith. Rings H13- |33 attached to enlarged ends |34- |$4 of the sleeve |80 secure the sleeves ||l| and |02 to the sleeve IBD for longitudinal movement therewith. This longitudinal movement of the sleeve |20 is effected by means of a key |05 (Figs. ll, 13 and 14) xed to a manually slidable rod |36 (Fig. 4) mounted in an axial aperture |61 in the shaft 23, the rod having an operating handle |88 atits outer end. The key |65 extends laterally from the rod |36 into opposite apertures |29 in the sleeve |62 and is reciprocable in a slot ||2 in the shaft 23 and thus the sleeve |32, although movable longitudinally with the sleeve |533, which latter sleeve is rotatable relative to the shaft 23, is prevented from rotating relatively to the shaft 23. Similarly the sleeve ||i| is prevented from rotating with the sleeve |90 although movable longitudinally therewith by being keyed as indicated at ||3 to the shaft 23 (Figs. 13 and 14).

Upon its outer ends, the clutch sleeve It!) has fixed thereto toothed rings H4, each having a plurality of inwardly extending teeth l5, which are adapted to mesh with a plurality of teeth I6 on the periphery of the Oldham clutch bushings 97 upon longitudinal movement of the sleeve |50 in one direction or the other, the teeth H5' and HB being so spaced that they mesh only when the sleeve and bushings are predeterminedly angularly related, in which angular relation the eccentric bushings 42 and 43 are ,arranged relative to the eccentric shaft portions 40 and 4|, respectively, for zero eccentricity with respect to the axis of the shaft and thus the bushings will rotate with the shaft without imparting any movement to the table "52. Keyed, as indicated at |l9, to the concentric shaft portion 90 outside of and aligned with the ends of the Oldham" clutch bushings 91 are annular spacer or stop rings |20, which abut at one end annular shoulders on the adjacent ends of the central concentric portion S9 of the shaft 23. The clutch` bushings? each have formed on their inner end faces a plurality of teeth |2|, which are adapted to mesh with a plurality of teeth |22 on the adjacent end faces of the flanged sleeves and |02V when the sleeve |00 is moved longitudinally to the limit of its movement in either direction, in which positions the sleeves abut the stop rings |20, the movement of the sleeve |00 being effected by a shifting of the manually operated rod |05. The relation of the teeth I2| and |22 at the termination of these movements of the sleeve |00 is clearly shown in Figs. 13 and 14.

In Figs. 4 and 13, the clutch sleeve I 00 has been shifted to its extreme leithand position and, consequently, the teeth |22 of the sleeve |0| are meshed With the teeth |2I on the clutch bushing 91 of the Oldham clutch 85 and the teeth ||5 movable with the clutch sleeve |00 have been moved out of mesh with the peripheral teeth IIS on the bushing 91 of the coupling 85. The alignment of the teeth |2I and |22 for meshing is insured since the previously intermeshecl teeth H5 and ||6 are disengaged as the teeth I 2| and |22 are engaged. With the sleeve |00 in this position, it will also be observed that the teeth |22 of the right hand sleeve |02 are out of mesh with the teeth |2| lon the clutch bushing 91 of the Oldham" clutch 88 and the right hand teeth I I5 movable with the clutch sleeve |00 are in mesh with the peripheral teeth IIS on the right hand bushing 9T. When the clutch sleeve |00 is thus positioned (Figs. 4 and 13), the left hand eccen tric bushing 62 Will be locked against rotation with respect to the shaft 23 by the interengagement of the teeth |2| and |22 and in this position the eccentric bushing l2 will be arranged relative to the eccentric shaft portion l0 for zero eccentricityf with respect. to' the axis of the shaft and thus the bushing |52, in the operation of the apparatus, will rotate with the shaft without imparting any horizontal movement to the table 52. Also, in this left hand position of the clutch sleeve Ill-0 (Figs. 4 and 13), the right hand eccentric bushing 43, due to the teeth |22 of the right hand sleeve |02 being out of mesh with the teeth |2I on the clutch bushing B'l of the Oldham clutch 8S, is free to be adjusted about the eccentric shaft portion 4I to vary the effective eccentricityI of the bushing with respect to the axis of the shaft 23 by rotating the bushing with respect to the shaft for imparting vertical movement to the table 52.

Fig. 14 illustrates the relation and position of the parts illustrated in Figs. 4 and 13 when the clutch sleeve |00 has been shifted to its extreme right hand position, thus permitting the left hand eccentric bushing 42 of the Oldham clutch 85 to be adjusted Aabout the eccentric shaft portion 40 to-vary the effective eccentricity of the bushing 42 with respect to the axis of the shaft 23. by rotating the bushing with respect to the shaft and thereby imparting horizontal movement to the table y52 when the shaft rotates.

For the purpose of adjusting the eccentric bushings 42-y and 43 during operation of the apparatus, when the bushings are free to be adjusted, as above described', the following mechanism is provided, Formed on the central shaft portion keyways 09 are right hand spiral threads |25 of suitable lead and lengt-h, on which is a, nut |26 having three equally spaced splines or keys |21 extending radially from its periphery (Figs. 4 and 12). The keys |21 are slidable in three similarly spaced keyways |28 formed longitudinally inthe clutch sleeve |00 and thus, when the nut |28 is shifted axially to the right upon the spiral threads |25 fromthe position shown in Fig. 4, with the teeth H4 and IIB in mesh, with respect to the'shaft 23, relative rotation Will be imparted to the sleeve |00 and, through the Oldham clutch 86, the eccentric bushing 43 will be rotated or adjusted with respect to the eccentric shaft portion 6|.

A ball bearing assemblage |20 has its inner race attached to the nut |28 and its outer race pivotally connected by means of trunnions |32 and |23 to a ring |34, which, in turn, is pivotally connected by means of trunnions |35 and |36 to a yoke |30, thus providing a universal coupling between the ball bearing assemblage and the yoke. The yoke |39 is provided with spaced irregularly shaped bearing blocks |40 and |4| (Figs. 3 and 5), which are keyed for movement longitudinally of a lxed shaft |42 secured at opposite ends to the side frame members 34 and the shaft carrying two diametrically opposed keys |23, which are entered in similarlyarranged l in the bearing blocks. Similarly keyed on the shaft |22 to the right of the bearing block. lili is an irregularly shaped slide block |47, which, in the operation of the apparatus, is reciprccated upon the shaft |42; Fixed to the shaft |02 intermediate the bea-ring blocks |00 and |4I is a collar |432 and surrounding the shaft between opposed faces of the collar and the bearing block IfiI is a compression spring |49, which normally urges the yoke |39 to the right (Figs. 3 and 5) Before it is possible to actuate the shift rod |06 to change direction of vibration of the table 52, it is necessary to bring the bushings 42 and 43 to a zero position of eccentricity. To accomplish this, there is provided a shouldered pin (Fig. 3) having a threaded portion threaded in the bearing blockv |l| ofthe yoke |30 and having a shouldered face |53 normally abutting the adjacent face of the slide block Il. At its outer end, the pin extends freely through an aperture in the side frame member 35 for engagement by a crank arm (not shown). Thus, to set the bushings 42 and 43 to zero eccentricity, the pin |50 may be rotated in a direction to advance an outer shouldered face 54 thereof into abutting relation with the inner face of the side frame member 35, after which a continued rotation of the pin will cause movement of the yoke bearing block Ii towards the left, as viewed in Fig. 3. This last described movement of the yoke bearing block lill and the parts movable therewith, which includes the nut |242 will continue until a stop screw |55 carried by the yoke bearing block |00 engages the inner face of the side frame member 3', At this point, due to the axial movement of the nut |26 along the shaft 23, the eccentric bushings 02 and i3 will have been brought to zero position and, as thus positioned, the rod It may be actuated to change the direction of vibration of the apparatus. When this has been effected, the pin |50 is returned to its normal position by rotating it in the opposite direction, with the shouldered face |53 abutting the adjacent face of the slide block |01, thus locking the slide block to the yoke |39 so that they will reciprocate in unison at all times in the operation of the apparatus. It will be understood that the stop screw |55 is predeterminedly adjusted and set in the initial set-up of the apparatus.

From the foregoing, it is believed to be apparent that the table 52 may be reciprocated optionally in a vertical or horizontal direction, dependent upon the position of the manually operab-le rod |96, the position of which determines which of the eccentric bushings 42 and 43 is set for driving the table 52. Also, by varying the effective eccentricity of the eccentric bushings 42 and 43 with respect to the axis of the rotatingl shaft 23, the table 52 will be vibrated through predetermined distances by the driving of one of the bushings, while the other bushing is set for zero eccentricity. The varying of the eccentricity of either of the bushings 42 and 43, it will be noted, is effected by a movement of the yoke |39 longitudinally of the shaft 23. This movement of the yoke |39 will result in a movement of the nut |26 on the spiral threads |25 of the shaft. Thus, by means of the sleeve connected to the nut |25 and the coupling between the sleeve and the particular eccentric bushing set for driving the table 52, a relative rotation will be obtained between the nut and the shaft 23 and thereby a turning of the eccentric bushing on the eccentric portion of the shaft.

The above-described apparatus is capable of being operated to cause, as hereinbefore referred to, either vertical or horizontal vibrations of selected amplitudes of the table 52 in either of two ways, that is, to operate at a constant or fixed amplitude and a varying rate of frequency, or to operate at a constant acceleration over a selected range of frequency. Also, in the rst of these two ways of operation, mechanism is provided for compensating for the inherent elasticity of the various members connecting the shaft 23 to the table 52, whereby the constancy of amplitude of vibrations of the table may be controlled with a high degree of accuracy while varying the rate of vibration by changing the speed of the main drive motor 2| for the apparatus.

Reciprocation of the yoke |39, which, as before described, controls the amplitudes of vibrations of the table 52, is effected by a main control lever $51 (Figs. 3 and 5) pinned at |58 to the slide block M1, which, in the manner previously described, is locked to the yoke |39. Fixed to the lever |51 is an irregularly shaped extension lever' |59. With this combination of levers |51 and |59, and the associated mechanism to be presently described, the apparatus is set up to vibrate the table 52 at a xed amplitude and at a varying rate of vibration and to compensate for the elasticity of the various operative connections between the shaft 23 and the table 52.

At its outer end, the extension lever |59 is split to receive and clamp, as indicated at |89, an adjustable bearing bushing |5| in any selected position of rotation. The bushing |6| has a flange at its upper end (Fig. 6) and formed eccentrically in and extending through the bushing is a circular aperture |52 for freely receiving a cylindrical portion of a sleeve |63 having a flange at its lower end. Between the flange of the sleeve |55 and the lower surfaces of the bushing |5| is washer having an eccentrically formed aperture which also engages the lower surface of lever |59 and which is maintained in alignment with the eccentric aperture |52 in the bushing by securing the Washer and bushing together in a suitthe shaft is effected and, consequently, the amvable manner after assemblage so that they may be rotated as a unit to a selected position. Fitted in the aperture of the sleeve |63 and the aperture in the lower washer is a cylindrical portion of a headed pin |54, which is provided with two substantially ilat surfaces adapted to engage surfaces of an arcuately formed slot |55 formed in a lever |56 pivoted on a rod |51 carried on the frame of the apparatus. At its upper end, the pin |54 is screw-threaded to receive a nut, by means of which, together with a washer bearing on the upper annular end surface of the sleeve |63 andv a lower head on the pin, the sleeve, the pin, and the lever |56 may be clamped together as a unit with the bushing |6| free to rotate upon the periphery of the sleeve .in the operation of 'the apparatus. It will be apparent that by loosening the clamp screw |60, the bearing bushing |5| may be rotated on the extension lever |59 to a selected position and, due to its eccentric bearing on the sleeve |63, the extension lever |59 and the attached lever |51 and the parts movable therewith, including the nut |25, will be shifted longitudinally.

The free end of the lever |55, previously mention'ed, carries a cam roller |58, which rides on the peripheral surface of a rotatable cam |59 under the urging of the compression spring |45. rIfhe cam |69 is carried upon a shaft |18` having an eccentric portion |'1|, the purpose of which will be l described hereinafter. The shaft |19 is driven through a train of gears |12 and |13 (Figs. 1 and 2) from a gear reducer |14 driven by belt and pulleys, indicated at |15, in turn driven by a reversible constant speed electric control motor |11. Thus, upon rotation of the camn |69, the lever |66 will be oscillated about the rod |51 and motion will be transmitted through the levers |59 and |51 to the yoke |39 to shift the nut |25 axially along the spiral thread |25 of the shaft 23. When the nut |26 is shifted axially of the thread |25, relative rotation will be effected between the shaft 23 and either or both of bushings 112 and d3, depending upon the position of the rod |58. In this manner, when the nut |26 is moved axially of the shaft 23, a gradual variation of the effective eccentricity of the driving portions of plitude of the vibrations of the table 52 will be gradually varied in a selected range determined by the area and amplitude of movement of the nut |26. The amount of reciprocation imparted to the combined levers |59 and |51 will depend upon the position of the pin |54 along the slot |55 of the lever |55 and the particular contour of the cam |69, the pin being predeterminedly adjusted and clamped in position.

It will be understood that with an accurate adjustment of the bushing |6| in the lever eXtension |59 and an accurate setting of the pin |6ll along the slot |65 of the lever |55, in combination with a predetermined contour of the cam |89, the required change in the effective eccentricity of either of the bushings 42 and 43 may be had to compensate for the change in overthrow of the table 52 during its movements due to the elasticity of the various members connecting the shaft 23 to the table 52 as the rate of vibration changes.

The speed of the main drive motor 2|, which determines the frequency of vibrations of the table 52, is controlled by a potentiometer, indicated in general at |18 (Fig, 2), having a brush |19 movable back and forth across a fixed surface or winding of the potentiometer. A potentiometer controlling cam |8| is secured to the low speed shaft of the speed reducer |14 and is thus driven from the reversible constant speed electric control motor |11. A cam roller |811 engaged by the cam 18|, and mounted to move with the brush |19, drives the brush in one-direction across the winding |89 of the potentiometer |18. The winding |81) is connected in circuit with the main drive motor 2| and controls the speed of this motor, thereby regulating the frequency of vibrations imparted to the table 52. The cam roller |84 is constantly urged against the cam I8| by means of a suspended weight |85, which also serves to move the brush ina direction opposite to said one direction under the control of the cam |8|, the weight being attached to one end of a flexible member |85 guided over pulleys |81 and attached at its opposite end to the mounting which supports the cam roller |84 and the brush |19.

The operation f the reversible motor |11 is under control of a pair of motor reversing microswitches I9!) and |9| and an intermediate limit or motor cut-ont switch |92, which are, in turn, controlled by three roller-type actuators |93, |94 and |95, respectively. Fixed to the shaft which carries the potentiometer controlling cam |8| are two adjustable switch-controlling arms |98 and |99 having arcuate shaped outer ends adapted to alternately engage the switch actuators |93 and |94 of the switches |90 and |9I, respectively, to reverse the supply oi current to the control motor |11, thus to reverse the direction of rotation of the main control lever cam |69 and the, potentiometer cam i8 In their positions shown in Fig. 1, the arms |98 and |99 have been vrotated clockwise and the arm |93 has just actuated the microswitch I9! and, consequently, the rotation of the two arms and the associated potentiometer controlling cam |8| will be initiated in a counterclockwise direction to cause the arm |99 to actuate the microswitch |90. Thus, the drive to the cams |69 and |8I, which control the range of. amplitude and frequency of vibrations of the table 52 will again be reversed. The switch |92, which is included in the circuit to the motor |11 and arranged in the path of either of the arms |98 and |99, serves, in case the microswitches |99 and |9| fail at any time, to completely break the supply of current to the motor. In addition, vibrating in either av horizontal or a vertical path, as above described, the table 52 may also be driven through circular paths of varying diameters. To provide for this latter type of movement, the eccentric shaft portions 40 and 4l are oifset 90 from one another, as hereinbefore described. Thus, the manually operable rod |06 may be slid to a position intermediate its extreme 4left and right hand positions, as clearly shown in Figs. 13 and 14, and in such intermediate position, the right and left hand eccentric shaft portions 4| and 40 will both be clutched to their associated eccentric bushings 43 and 42, respectively, as indicated in dotted lines in Fig. 14. This referred-to intermediate position of the rod |96 will slide the clutch sleeve |89 to the fragmentary broken outline position indicated at 299 in Fig. 1.4, in which position each of the eccentric shaft portions d and di lare clutched by means of the teeth |15 carried on opposite ends of the clutch sleeve HJG meshincr with the teeth H on the Oldham clutch bushings 91, as shown inbroken outline, and in this position the teeth l2! on the bushings 91 are disengaged from the teeth |22 on the flanged sleeves ||l| and |02., which sleeves move longitudinally with the clutch sleeve |99.

Thus, in the operation of the apparatus, both of the eccentric bushings 42 and G3 will be driven and since the eccentric shaft portions 49 and 4| are offset the table will be vibrated through a circular path. Suitable locking means (not shown) may be provided for retaining the manually shiftable rod |96 in each of its three positions.

Fixed to and reciprocating with the yoke bearing block lill is a pointer 252, which is mounted for movement outside a forward frame member 293 of the apparatus (Figs. 2', 3 and 7) the pointer cooperating with a scale plate 2&5 attached to the frame member. In the operation of the apparatus, the pointer 292 and the scale plate Will indicate the amplitude of vibration of the table 52 at very low frequencies. At these low frequencies, it will be readily apparent there is practically no overthrow due to elasticity. At higher frequencies, th'e scale and pointer will provide, by its movement, an indication of the degree of compensation being effected due to elasticity by moving to the left to indicate the reduction in eccentricity which is necessary to compensate for the increased overthrow at higher frequencies.

One operative arrangement of the above-described apparatus will now be described as i1- lustrative of one mode of operation of the apparatus. `If it be assumed that it is desired to impart vertical vibrations to a piece of apparatus mounted on the table 52 and suitably iixed thereto, and if it be assumed that the apparatus tc be tested is to be subjected to vibrations over fixed amplitudes at a gradually decreasing rate from, for example, 60 cycles to nearly 0 cycles per second and, at the same time, it is desirable to compensate for the elasticity of the various operative connections between the shaft 23 and the table 52, the apparatus is set up as shown in Figs, 1 to 9, inclusive, and Figs. 12, 13 and 14. As hereinbefore described, and as shown in Figs. 4 and 13, the manually operable rod has been moved to such a position that the right hand eccentric portion 4| of the shaft 23 has been clutched to its associated eccentric bushing i3 and thus vertical vibrations of the table will occur upon rotation of the shaft, the left hand eccentric portion 99 of the shaft being unclutch'ed from its associated eccentric bushing 132 and set to zero eccentricity with respect to the axis of the shaft and locked against rotation with respect thereto in a manner previously described. In addition to this shifting of the rod |96, the cam |69, which has a predetermined peripheral contour for shifting the main control lever |51, is mounted upon the shaft |19. It is to be understood that the position of the pin I in the slot |55 of the lever |96 determines the length of throw of the main control lever |51 and thus the throw cr axial movement of the amplitude control nut |25 effected by the movement of the lever |51. The closer the pin |54 is set to the cam roller |953, the greater will be the throw and, hence, the greater the degree of compensation effected. Obviously, `as the frequency changes, the eccentricity must also be changed since at higher frequencies the overthrow is greater, while at lower frequencies it is less due to the elasticity in the operative connections between the shaft 23 and the table 52. Thus, on increasing speed, the eccentric bushing will be rotated closer to the zero position, and vice versa. Rotary adjustment of the eccentric bearing I6! changes the points of reversal of the nut |26 without changing the shift distance controlled by the position of the pin |84 in the 13 slot |65 of the lever |66. In addition to the above adjustments and set-up, the potentiometer controlling cam ll is secured to the slow speed shaft of the speed reducer |74 in proper relation to the predeterminedly adjusted switch controlling arms |8 and |99. The arms |98 and |99, in cooperation With the switches |92 and |9|, serve to control the reversal of the supply of current to th`e control motor |71 and thereby the direction of rotation of the main control lever cam |69 and the potentiometer cam |8|.

With the apparatus set up as above described to impart vertical vibrations to the table 52, the motors 2| and ill are started, As the motor 2| drives the shaft 23, the motor |11 will be drivingr the cams |69 and 18| back and forth through a rotary path so as to cause change in amplitude and frequency of vibrations, respectively, of the table with the compensating mechanism functioning in the manner previously described to compensate for the elasticity of the operative connections between the shaft 23 and the table 52 with a high degree of accuracy.

When it is desired to use the above-described apparatus to test articles at a constant rate of acceleration over a selected range of frequency and to maintain the selected rate of acceleration constant, changes are made in its set-up as follows: The extension lever |59 is detached from the main control lever |57 (Figs. 10 and 11) and replaced by a split extension lever 295, which is rotatably secured to the eccentric portion '1| of the shaft |78 in a manner similar to that of the extension lever |58 to the pin |56. Also, with these changes in the set-up of the apparatus, the lever |66 is not necessary and is removed. Thus, in the rotation of the shaft |79 and the resultant crank action of the eccentric shaft portion the combined levers |51 and 285 will have imparted thereto oscillatory and reciprocatory motions. The eccentricity of the eccentric bushings l2 and 43 relative to the axis of the shaft 23 will, therefore, be varied over a selected range to thereby control the amplitude of vibrations of the table 52. The speed of the main drive shaft 23 is under control of the potentiometer cam ISI, which is so designed that the speed of the motor 2| will vary in such a way as to bear a denite mathematical relation to the amplitude of vibrations of the table co-ntrolled by the position of the eccentric portion |'l| of the shaft |18 and so result in a constant rate of acceleration of the table.

What is claimed is: ,l

l. In a controller for a vibrating apparatus, a vibratory means, a main drive shaft having an eccentric portion, an eccentric bushing mounted on said eccentric shaft portion, an operative connection between said bushing and vibratory means, a screw connection between the shaft and bushing for varying the angular position of the bushing relative to the eccentric shaft portion, means for controlling the speed of the shaft, and means interconnected with said last-mentioned means for setting said screw connection in accordance with the speed of the shaft, said last-mentioned means including a link and lever mechanism connectible to adjust said screw connection to compensate for changes in amplitudes of vibration of said vibratory means due to elasticity of said operative connection.

2. In a controller for a vibrating apparatus, a vibratory means, a main drive shaft having an eccentric portion, an eccentric bushing mounted on said eccentric shaft portion, an operative connection between said bushing and vibratory means, a screw connection between the shaft and bushing for varying the angular position of the bushing .relative to the eccentric shaft portion, means for controlling the speed of the shaft,

and means associated with said last-mentioned means effective to adjust said screw connection in accordance with the speed of the shaft to compensate for changes in amplitude of vibration of said vibratory means due to elasticity of said operative connection and thereby maintain the amplitude of the vibratory means constant.

3. In a vibrating apparatus, a vibratory means to be vibrated; means for vibrating said vibratory means in a predetermined path including means for varying the frequencyand amplitudesl of vibrations imparted by the vibrating means to the vibratory means, an operative connection between said Vibrating means and said vibratory means, means interconnected with the frequency varying means for varying the amplitudes of vibrations of the vibratory means in accordance with the frequency thereof, and means associated with said last-mentioned means effective to adjust said means for varying the amplitudes of the vibrations in accordance with the frequency thereof to compensate for changes in amplitude of vibration of said vibratory means due to elasticity of said operative connection and thereby maintain the amplitude of the vibratory means constant.

4. In a vibrating apparatus, a main drive shaft,

ieans for driving said shaft, means for varying the speed of said driving means in accordance with a predetermined pattern, vibratory means. a pair of eccentric surfaces on said shaft, eccentric bushings on said surfaces, means interconnecting said bushings and vibratory means, means on said shaft intermediate said surfaces for varying the angular position of said bushings relative to the eccentric surfaces of said shaft to vary the amplitudes of vibrations of said vibratory means, and means interconnected with said last-mentioned means on said shaft for setting said means on the shaft in accordance with the speed of said shaft, said interconnected means being connectible to adjust said means on the shaft to compensate for changes in amplitude of said vibratory means due to elasticity of said means interconnecting said shaft and vibratory means.

5. In a vibrating apparatus, a table, a plurality of levers for supporting said table, compound eccentrics for actuating said levers to impart amplitudes of vibrations to said table, means for varying the effective eccentricities of said eccentrics, a drive shaft common to said eccentrics, means interconnected with the means for varying the effective eccentricity of the eccentrics for varying the speed of the shaft, and means including an element coaxial with the shaft and optionally settable longitudinally of said shaft to render one of said compound eccentrics ineffective.,

6. In a vibrating apparatus. a main drive shaft, means for driving shaft, means for varying the sneed of said driving means, vibrator-y means, variable operative connections between said shaft and vibratory means, means for varying said connections in accordance with a predetermined pattern, and means associated with said speed varying means effective to adjust said variable operative connections in accordance with the speed to compensate for changes in amplitude of vibration of said vibratory means due to elasticity of said variable operative connections and the eby maintain the amplitude of the vibratory means constant.

'7. In a vibrating apparatus, a vibratory means for supporting articles to be vibrated, a rotary drive shaft, means operatively associated with and driven from said shaft for vibrating said vibratory means in either of severa-l selected paths, means for varying the frequency and amplitudes of vibrations imparted to the vibratory means, means for maintaining the peak acceleration or the vibratory means constant as the amplitudes and frequencies thereof are varied, an element surrounded by said shaft and coaxial therewith and settable longitudinally of said shaft to select the path of vibration of said vibrating means, and an operative connection between said element and said means for vibrating said vibrator-y means.

8. In a vibrating apparatus, vibratory means for carrying articles to be vibrated, a main drive shaft, a pair of compound eccentric means driven by said shaft comprising eccentric portions on said shaft and eccentric bushings surrounding said eccentric portions of the shaft for vibrating the vibratory means in several paths, control means for varying the relative rotative position of said eccentric portions and their associated bushings, shftable means surrounding said shaft for selectively connecting an eccentric bushing to said control means, an actuator for said shiftable means mounted in an axial aperture of the shaft and settable longitudinally thereof, and a connection from said actuator to said shiftable means operable through a radial opening in the shaft.

9. In a vibrating apparatus, a vibratory means to be vibrated, variable means for vibrating said vibratory means, a variable speed motor for ldriving said vibrating means, an operative connection between said vibrating means and said vibratory means, and means for varying the action of said vibrating means to compensate for inherent elasticity between said vibrating means and said vibratory means including a driven cam, a cam lever oscillatable about a fixed pivot'by said cam, an adjusting lever for varying the vibratory action of said vibrating means on said vibratory means, and means for operatively connecting said adjusting lever to said cam lever at a selected position on the cam lever to vary the action of said adjusting lever on said vibrating means in accordance with the speed of the motor.

10.1n a vibrating apparatus, a vibratory means to be vibrated, variable means for vibrating said vibratory means. a variable speed motor for driving said vibrating means, an operative connection 1between said vibrating means and said vibratory means, and means for varying the action of said vibratingmeans to compensate for inherent elasticity between said vibrating means and said vibrator-y means including a driven cam, a cam lever driven by said cam, an

adjusting lever for varying the vibratory action of said vibratingmeans on said vibratory means, means for operatively connecting said adjusting lever to said vibrating means comprising reciprocatory elements movable in spaced parallel paths, and a unive sal joint connect-ing said elements.

1l. In a vibrating apparatus, a vibratory means to .be vibrated, variable means for vibrating said vibratory means, a variable speed motor for driving said vibrating means, an operative connection between said vibrating means and l@ said vibratory mee-ns, and means for varying the action of said vibrating means to compensate for inherent elasticity between said vibrating means and said vibratory means including a driven cam, a cam lever driven ov said an. adjusting lever for varying the vibratory action or" said vibrating means, means for operatively connecting said adjusting lever to said vibrating means comprising eciprocatory elements movable in spaced parallel paths, a universal ici connecting said elements, and means for o atively connecting said adjusting lever to said cam lever at a selected position on the cam lever to vary the action of adiusting lever on said vibrating means in accordance with the speed of the motor.

l2. In a vibrating apparatus, a vibratory means to be vibrated, variable means for vibrating said vibratory means, a variable speedI` motor for driving said vibrating means, means for operatively connecting 'vibrating means to said vibratory means, and means for varying the action of said vibrating means to compensate for inherent elasticity between said vibrating means and said vibratory means including a driven cam, a cam lever driven by said cam, an adjust*- ing lever for varying the vibratery action of said vibrating means on said vibratcry means, means for operatively connecting said adjusting lever to said cam lever a selected position on the cam lever to vary the action cf said adjusting lever on said Vibrating means in accordance wit the speed of the motor, and means associated with said means for operatively connecting seid adjusting lever to said cam lever for varying the position of said adjusting lever without changing said selected position oi connection of said ad justing lever with said cam lever.

13. In a vibrating apparatus, a vibrator-y table, a main drive shaft, a variable s eed motor for driving said shaft, variable eccentric lies on said shaft for reciprocating the table, and means for controlling the eccentricity of assemblies to compensate for inherent elasticity in the connections between the eccentrics and table including a driven cam, a cam lever driven by said cam, an adjusting lever for said assemblies, and a link extending from said adjusting lever and connectible to cam lever at a selected position on the cam lever for adjusting the eccentricity of the assemblies in accordance with the speed ci the moto".

14. In a vibrating apparatus, a vibratory means to be vibratcd, variable means for vibra said vibratory means, a variable speed motor for driving said vibrating means, an arm connec; to said vibrating means, a multiple lever and lids mechanism between said arm and said Vibratoiy means, and means for varying the action of said vibrating means to compensate lor inherent elasticity between said vibrating means and said vibratory means including a driven cam, a cam lever driven by said cam, an adjusting lever for varying the vibratory action of said vibrating means on said vibratory means, and means for operatively connecting said adjusting lever to said cam lever at a selected position on the cam lever to vary the action, of said adjusting lever on said vibrating means in accordance with the speed oi the motor.

15 In a vibrating apparatus, a vibratory means to be vibrated, a main driving shaft having an eccentric portion, an eccentric bushing mounted on said eccentric shaft portion, a bearing ring surrounding said eccentric bushing, and an oper- 2,438,756 17 18 atve connection between said bushing and vibra.- REFERENCES CITED tory means including an arm extending from said bearing ring, a pair of levers each connected at lrghf gvgtgefns are of record m the one end to Said arm and extending in opposite directions, and a `pam' of links each connected 5 UNITED STATES PATENTS at one end to each of the opposite ends of said Number Name 'Date levers, said links being connected at their op- 2348189 Buchanan et L May 9 1944 7{ 15 1; posite ends to said Vibratory means. n 2,399,503 Ott APL 30, 1946 if 'ff 1,901,122 Robins Mar. 14, 1933 if I; K EINER W- LARSEN 1 2,232,124 Markley Feb, 18, 1941 i, c 1" n 

